Coal loader



D. L. STACY July 2, 1968 COAL LOADEB I 4 Sheets-'Sheet 1 Filed May 19. 1967 David L. Stacy INVENTOR.

D. L. STACY COAL LOADER July 2, 1968 4 Sheets-Sheet 2 Filed May 19, 1967 David L. Stacy INVENTOR.

D. L. STACY July 2, 1968 COAL LOADER 4 Sheets-Sheet 5 Filed May 19, 1967 mum bk Qm David L. Stacy INVENTOR.

D. l... STACY COAL LOADER July 2, 1968 4 Sheets-Sheet} Filed May 19, 1967 m. m Wm m mm. L m M a D Y United States Patent 3,390,755 COAL LOADER, David L. Stacy, Box 755, Grundy, Va. 24614 Filed May 19, 1967.5. No. 639,906 4 Claims. (Cl. 1989) ABSTRACT OF THE DISCLOSURE A mining machine for loading coal into a collection bin by means of a boom mounted conveyor extending rearwardly and upwardly from a lowered loading head from which the coal is displaced onto the conveyor by a pair of rotating loading arms that overlap the conveyor. The boom and head are pivotally mounted on a low height vehicle frame supported by rubber tired wheels driven by fluid motors. Separate drive motors operate the loading arms which are synchronized by a connecting drive that also operates the conveyor.

This invention relates to mining machines and more particularly to a coal loading vehicle propelled to a desired location within a mine so as to scoop coal particles onto a loading head from which they are displaced by rotating arms onto a conveyor, the conveyor transporting the coal to a rearward location from which it is deposited into a collection bin.

It is sometimes desirable to provide a coal loading machine of the aforementioned type which is of a relatively low height and small size for use in mines and at locations where space is very limited. Such a machine must also be capable of withstanding rough treatment and have a heavy duty capability. Also, the machine must be capable of being self-propelled and easily maneuvered without disturbance to the bottom of the mine.

In accordance with the present invention, a relatively small and low coal-loading vehicle is provided wherein a loading head extends forwardly from the vehicle and a conveyor boom extends rearwardly therefrom, both being pivotally mounted adjacent the forward end of the vehicle. Hydraulic piston devices are provided for lowering and elevating the head and boom while fluid motors are provided to propel and steer the vehicle frame under control of an operator through readily accessible hydraulic controls. Rubber wheels of the pneumatic type are utilized for propelling the vehicle without tearing up the bottom of the mine within which the vehicle is to be utilized.

The coal loading machine of the present invention also features separate drive transmissions for a pair of rotating loading arms mounted by the head and overlapping the boom mounted conveyor onto which the loading arms displace coal particles for transport to a location rearwardly of the loading vehicle. The drive transmissions for imparting rotation to the loading arms include shockabsorbing, shaft couplings of the yieldable type in order to avoid rupture of the transmission parts in the event of any overload. A positive drive however interconnects the loading arms for synchronization purposes as well as to impart movement to the boom-mounted conveyor driven at its lower end between the loading arms.

These together with other objects and advantages which will become subsequently apparent reside in the details of construction and operation as more fully hereinafter described and claimed, reference being had to the accompanying drawings forming a part hereof, wherein like numerals refer to like parts throughout, and in which:

FIGURE 1 is a top plan view of a coal loading machine constructed in accordance with the present invention.

FIGURE 2 is a side elevational view of the machine shown in FIGURE 1.

3,390,755 Patented July 2, 1938 FIGURE 3 is an enlarged transverse sectional view taken substantially through a plane indicated by section line 3-3 in FIGURE 2. 4

FIGURE 4 is an enlarged partial sectional view taken substantially through a plane indicated by section line 4-4 in FIGURE 1. v

FIGURE 5 is an enlarged partial sectional view taken substantially through a plane indicated by section line 55 in FIGURE 1.

FIGURE 6 is a schematic perspective view showing the operative interrelationship of 'various components associated with the coal loading machine.

Referring now to the drawings in detail, FIGURES 1 and 2 illustrate the entire coal loading machine generally referred to by reference numeral 10. The machine includes a vehicle frame generally denoted by reference numeral 12 which is rectangular in shape including an outer frame having the side portions 14 and 16 interconnected at the forward end by a front portion 18. Rear end portions 20 and 22 are formed at the rear end of the outer frame interconnected by the angle frame member 24. Posts 26 and 28 extend upwardly from the outer frame laterally spaced from each other on either side of the longitudinal axis of the machine so as to support guard rails 30 between which a boom assembly 32 extends upwardly from the forward end of the vehicle frame at which location it is pivotally mounted thereon. Also pivotally mounted by the vehicle frame adjacent its forward end, is a head structure generally denoted by reference numeral 34. Supporting platforms 36 and 38 extend between the forward and rear ends of the vehicle frame for supporting various operating components of the machine thereon as will be hereafter described. Rubber tired wheels 40 are rotatably mounted by the vehicle frame for support thereof above the ground adjacent the rear and forward ends. Four such wheels are illustrated which project downwardly from the vehicle frame between the supporting platforms 36 and 38 and the side portions 14 and 16 of the outer frame as more clearly seen in FIGURE 1.

The head assembly 34 includes a top deck portion 42 from which side portions 44 depend downwardly so as to pivotally mount the head assembly about an axis established by the pivot shaft 46 extending between the side portions 14 and 16 of the outer frame adjacent the forward end of the vehicle. Also pivotally mounted by the pivot shaft 46, is the forward end of the boom 32 from which the lower end of a conveyor assembly 48 projects into the cut-out 50 formed in the deck 42 of the head assembly. The conveyor assembly includes an endless conveyor chain 52 entrained about a drive sprocket assembly 54 at the lower end and a driven sprocket assembly 56 at its upper end with which a chain tightening adjuster 58 is associated. Pusher elements 60 are secured to the conveyor chain at spaced locations therealong for upward movement of coal particles along the floor 62 of the boom assembly. The particles are displaced onto the conveyor from the deck 42 of the head assembly by means of a pair of rotating arm assemblies 64 rotatably mounted by the head assembly on opposite lateral sides of the lower end of the conveyor assembly 48.

As more clearly seen in FIGURE 4, the head assembly 34 when in a lowered position forms a scoop onto which coal particles are displaced by forward movement of the vehicle. A ground-engaging plate portion 64 extends rearwardly from the forward end of the deck 42 therebelow in order to limit downward movement of the head assembly to its lowered position by means of the hydraulic piston assembly 66, the opposite ends of which are pivotally connected to the head assembly below the deck 42 and the forward end portion 18 of the frame. The

boom assembly 32 on the other hand is displaced between an elevated operative position as shown in FIGURE 2 with the rear delivery end 68 above a collection bin 70 and an inoperative lowered position by means of a pair of hydraulic piston cylinder devices 72 the opposite ends'of which are pivotally connected to the frame portions and 22 and the sides of the boom assembly. Thus, the coalloading machine may be conditioned for transport purposes. In the transport position, the head assembly 34 is elevated as shown by dotted line in FIGURE 2 While the boom assembly 32 may be lowered. In an operative condition, the head assembly is lowered to the position illustrated while the boom assembly is elevated that its delivery end 68 may deposit coal into the collection bin.

With continued reference to FIGURE 4, it will be observed that each of the loading arm assemblies 64 includes upper and lower sections 74 and 76 of an oil filled gear casing having bearings 78 and 80 rotatably supporting a driven shaft 82 to which a face gear 84 is secured within the gear casing. Also splined to the upper projecting end of the shaft 82, in enclosing relation to the upper section 74 of the: gear casing, is a rotating housing 84 to which a pair of displacing arms 86 are secured in 180 relation to each other. The gear casing sections 74 and 76 are bolted to each other and secured to the deck 42 of the head assembly and also rotatably mount therewithin a pinion gear 88 in constant mesh with the face gear 84 for transmitting rotation to the housing 84 and the displacing arms 86 projecting radially therefrom. A second pinion gear 90 meshes with the face gear 78 within the gear casing in 90 relation to the pinion gear 88 as more clearly seen in FIGURE 5.

Input drive is imparted to the loading arm assemblies 64 through the pinion gears 88 by separate transmissions 92 and 94 located on opposite sides of the boom assembly as more clearly seen in FIGURE 1 in order to cause rotation of the coal displacing arms 86 overlapping the lower end of the conveyor assembly 48. The pinion gears 90 form part of a synchronizing connecting drive between the two loading arm assemblies 64. Thus, each pinion gear 90 is connected to a shaft section 96 as shown in FIGURE 5 which in turn is coupled to one side of the drive sprocket assembly 54 by means of a tubular coupling sleeve 98 of noncircular cross-section. Thus, the face gears 78 associated with the loading arm assemblies must rotate at the same speed in opposite directions preserving the outof-phase relationship of the coal displacing arms 86 so as to avoid any interference therebetween. Power is however yieldably and separately transmitted to each of the loading arm assemblies by the transmissions 92 and 94. Each transmission includes an electric drive motor 100 drivingly connected to the input side of a reduction gear assembly 102 by a yieldable shaft coupling 104. Shaft couplings of this type are well known and are arranged to accommodate any misalignment between shaft sections as well as to absorb torsional vibration by storing and releasing energy during the transmission of torque between adjacent shaft sections. This form of flexible shaft coupling is disclosed for example in US. Pat. No. 2,648,958 and includes an elastically flexible member permanently clamped to rigid disks splined to the ends of the shaft sections so that torque is transmitted with substantially no loss of energy between the shaft sections. The output sides of the reduction gear assemblies 102 are connected through universal shaft assemblies to the pinion gears 88, the shaft assemblies including pivoted shaft sections 106 and 108 as shown in FIGURE 4.

A prime mover in the form of a relatively large electric motor 110 is mounted on the platform 38 of the vehicle frame on one side of the boom as shown in FIGURE 1, this motor being coupled to a fluid pump 112. The suction side of the pump is connected to a fluid reservoir tank 114 mounted between the forward and rear wheels on the side of the boom opposite the motor 110 while the pressure output side of the pump is connected to a control valve assembly 116 mounted by the side portion 16 of the frame. The control valve assembly includes a valve section 118 having a pair of manual valve actuator controls 120 and 122 through which the fluid piston devices 66 and 72 are respectively controlled in order to lower or raise the head assembly 34 and boom 32. The pressure discharge side of the pump 112 is also connected to the other valvesection 1240f the control valve assembly with which the control handles 126 and 128 are associated. The control valve handles 126 and 128 accordingly control operation of a pair of fluid motors 130 and 132 of the rotary type respectively supported on the platforms 36 and 38 on opposite lateral sides of the boom adjacent the rearend of the frame. The fluid motors 130 and 132 propel and steer the vehicle.

The output shaft associated with each fluid motor 130 and 132 is drivingly connected to-a reduction gear assembly 134 through a sprocket drive 136 while the output side of the reduction gear assembly is drivingly connected by the sprocket drive 138 to the rear wheels. A connecting sprocket drive 140 interconnects the rear and'forward wheels for simultaneous rotation. Eachwheel is rotatably mounted on a stationary axle 142 secured by a lock plate 144 to the side frame portions 14 and 16 as more clearly seen in FIGURE 2.

Electrical energy is brought to the machine from an external source by means of an electrical cable 146 secured to the rear end of the vehicle by a clamp 148 so as to preventundue tension from being applied to the cable. The electrical cable is wired to the drive motors 100 and motor 110 through a control switch 150 for regulating operation of the prime mover motor 110 and a push button switch assembly 152 for regulating operation of the drive motors 100. Associated with the push button switch 152, is a starting box 154 by means of which starting and stopping of the motors 100 is effected and de-energization of the motors is automatically effected under overload conditions. Starting control boxes of this type are well known such as one manufactured by Westinghouse Corporation, referred to by catalog No. 11200k2cnn.

From the foregoing description, and with reference to FIGURE 6, the arrangement of parts and operation of the machine will be apparent. It will be appreciated therefore, that because of the pivotal mounting of the head assembly 34 and boom assembly 32 adjacent the forward end of the vehicle frame, it may be moved to a desired location through mines having very little head room. Further, because of the use of rubber tires, a minimum disturbance to the floor of the mine will be effected. Also, operation of the machine from one side thereof through the control valve assembly 116 may be accomplished in a facile manner and without requiring any great skill. Coal displacing operation of the loading arm assembly 64 and the conveyor 48 may be effected by drive transmission trains which are independent of the propelling and steering drives for the vehicle frame. By use of separate drives for the respective loading arm assemblies, relatively heavy loads may be accommodated without any danger of breakage to the transmission parts because of overload. Toward this end, the yieldable couplings 104 are utilized and the loading arm assemblies synchronized by a connecting drive which also operates the conveyor 48.

The foregoing is considered as illustrative only of the principles of the invention. Further, since numerous modifications and changes will readily occur to those skilled in the art, it is not desired to limit the invention to the exact construction and operation shown and described, and accordingly all suitable modifications and equivalents may be resorted to, falling within the scope of the invention as claimed.

What is claimed as new is as follows:

1. In a loading machine having a frame, pneumatic wheels supporting the frame, a rearwardly extending boom, a forwardly extending loading head, a pair of loading arms rotatably mounted by the head on opposite lateral sides of the boom, a conveyor mounted by the boom, drive means for rotating the loading arms and operating the conveyor comprising a pair of drive motors, a pair of yieldable coupling means continuously connected between said drive motors and the loading arms, synchronizing drive means interconnecting said loading arms and driving the conveyor within the loading head, and a propelling motor drivingly connected to the pneumatic wheels independently of said drive motors, each of said coupling means including adjacent shaft sections and an elastically resilient member permanently connected between the adjacent shaft sections to absorb torsional vibrations by storing and releasing energy while transmitting torque with substantially no loss of energy.

2. In a loading machine having a wheeled frame, a rearwardly extending boom, a forwardly extending loading head, means pivotally mounting the boom and the loading head on the frame adjacent a forward end thereof, fluid operated devices mounted by the frame adjacent said forward end and a rear end for elevating and lowering said boom and head respectively, a pair of loading arms rotatably mounted by the head laterally of the boom, a conveyor mounted on said boom extending beyond said forward and rear ends of the frame, pneumatic traction wheels rotatably mounted by said frame rearwardly of the pivotal mounting means and projecting thereabove on opposite lateral sides of the boom, a power operated drive mechanism for operating the fluid operated devices, the loading arms and propelling the frame, said drive mechanism comprising a pair of drive motors fixedly mounted by the frame on opposite lateral sides of the boom, a pair of torsionally yieldable transmissions drivingly connecting the drive motors to the loading arms, positive synchronizing drive means interconnecting the loading arms and drivingly connected to the coneveyor for operation thereof, a prime mover mounted by the frame on one lateral side of the boom, propelling means energized by the prime mover for rotating the traction wheels to propel and steer the frame, and control means operatively connecting the prime mover to the propelling means and the fluid operated devices, said prime mover including a motor driven pump on said one lateral side of the boom, a reservoir of fluid mounted by the frame on the other side of the boom, and fluid conduits connecting the reservoir to the pump and the pump to the control means on said one side of the boom.

3. In a loading machine having a wheeled frame, a rearwardly extending boom, a forwardly extending loading head, means pivotally mounting the boom and the loading head on the frame adjacent a forward end thereof, fluid operated devices mounted by the frame adjacent said forward end and a rear end for elevating and lowering said boom and head respectively, a pair of loading arms rotatably mounted by the head laterally of the. boom, a conveyor mounted on said boom extending beyond said forward and rear ends of the frame, traction wheels rotatably mounted by said frame rearwardly of the pivotal mounting means and projecting thereabove on opposite lateral sides of the boom, a power operated drive mechanism for operating the fluid operated devices, the loading arms and propelling the frame, said drive mechanism comprising a pair of drive motors fixedly mounted by the frame on opposite lateral sides of the boom, a pair of independent transmissions drivingly connecting the drive motors to the loading arms, synchronizing drive means interconnecting the loading arms and drivingly connected to the conveyor for operation thereof, a prime mover mounted by the frame on one lateral side of the boom, propelling means energized by the prime mover for rotating the traction wheels to propel and steer the frame, and control means operatively connecting the prime mover to the propelling means and the fluid operated devices, said prime mover comprising an electric motor, a pump driven by the motor on said one side of the boom, a reservoir of fluid mounted by the frame on the other side of the boom between the wheels and fluid conduits connecting the reservoir to the pump and the pump to the control means on said one side of the boom between the wheels.

4. The combination of claim 3 wherein each of said independent transmissions includes a reduction gear assembly, yieldable coupling means connecting the gear assembly to one of the drive motors and a universal shaft assembly drivingly connecting the gear assembly to one of the loading arms.

References Cited UNITED STATES PATENTS 1,796,943 3/1931 Pratt l989 2,208,128 7/1940 Holbrook et al. 198-9 X 2,282,704 5/1942 Butters 19810 2,392,697 1/1946 Russell et al. 198l0 3,116,914 1/1964 Young et al. 198-109 3,317,022 5/1967 Bennett et al. 198-10 EVON C. BLUNK, Primary Examiner. HUGO O. SCHULZ, EDWARD A. SROKA, Examiners.

R. J. HICKEY, Assistant Examiner. 

